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WO2019017149A1 - Dispositif de climatisation de véhicule - Google Patents

Dispositif de climatisation de véhicule Download PDF

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Publication number
WO2019017149A1
WO2019017149A1 PCT/JP2018/023916 JP2018023916W WO2019017149A1 WO 2019017149 A1 WO2019017149 A1 WO 2019017149A1 JP 2018023916 W JP2018023916 W JP 2018023916W WO 2019017149 A1 WO2019017149 A1 WO 2019017149A1
Authority
WO
WIPO (PCT)
Prior art keywords
air
heat exchanger
air conditioning
refrigerant
outdoor heat
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Ceased
Application number
PCT/JP2018/023916
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English (en)
Japanese (ja)
Inventor
竜 宮腰
耕平 山下
Current Assignee (The listed assignees may be inaccurate. Google has not performed a legal analysis and makes no representation or warranty as to the accuracy of the list.)
Sanden Automotive Climate Systems Corp
Original Assignee
Sanden Automotive Climate Systems Corp
Priority date (The priority date is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the date listed.)
Filing date
Publication date
Application filed by Sanden Automotive Climate Systems Corp filed Critical Sanden Automotive Climate Systems Corp
Publication of WO2019017149A1 publication Critical patent/WO2019017149A1/fr
Anticipated expiration legal-status Critical
Ceased legal-status Critical Current

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Classifications

    • B—PERFORMING OPERATIONS; TRANSPORTING
    • B60—VEHICLES IN GENERAL
    • B60H—ARRANGEMENTS OF HEATING, COOLING, VENTILATING OR OTHER AIR-TREATING DEVICES SPECIALLY ADAPTED FOR PASSENGER OR GOODS SPACES OF VEHICLES
    • B60H1/00—Heating, cooling or ventilating [HVAC] devices
    • B60H1/22—Heating, cooling or ventilating [HVAC] devices the heat being derived otherwise than from the propulsion plant
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F24—HEATING; RANGES; VENTILATING
    • F24F—AIR-CONDITIONING; AIR-HUMIDIFICATION; VENTILATION; USE OF AIR CURRENTS FOR SCREENING
    • F24F11/00—Control or safety arrangements
    • F24F11/30—Control or safety arrangements for purposes related to the operation of the system, e.g. for safety or monitoring
    • F24F11/41—Defrosting; Preventing freezing
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F25—REFRIGERATION OR COOLING; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS; MANUFACTURE OR STORAGE OF ICE; LIQUEFACTION SOLIDIFICATION OF GASES
    • F25B—REFRIGERATION MACHINES, PLANTS OR SYSTEMS; COMBINED HEATING AND REFRIGERATION SYSTEMS; HEAT PUMP SYSTEMS
    • F25B47/00—Arrangements for preventing or removing deposits or corrosion, not provided for in another subclass
    • F25B47/02—Defrosting cycles

Definitions

  • the present invention relates to a heat pump type air conditioner for air conditioning a vehicle cabin of a vehicle.
  • the refrigerant evaporates in the outdoor heat exchanger and absorbs heat from the outside air, so frost formation occurs on the outdoor heat exchanger. If the operation of the compressor is continued in a state where frost formation on the outdoor heat exchanger has progressed, the heat absorption capacity from the outside air is reduced, so that the operation efficiency is significantly reduced. So, conventionally, the situation of frost formation was judged from temperature, pressure, etc. of an outdoor heat exchanger, and defrosting of the said outdoor heat exchanger was performed. Therefore, there is a drawback that control of frost determination is complicated. In addition, conventionally, when defrosting the outdoor heat exchanger, the heating mode is stopped and there is a problem that the comfort is impaired.
  • the present invention has been made to solve such conventional technical problems, and it is relatively easy to reduce the comfort in the vehicle interior and to reduce the operating efficiency caused by the frost formation on the outdoor heat exchanger.
  • An object of the present invention is to provide a vehicle air conditioner that can be suppressed by control.
  • the air conditioner for a vehicle heats the air supplied from the air flow passage to the vehicle compartment from the air flow passage by radiating the refrigerant and the air flow passage through which the air supplied to the vehicle is circulated.
  • a radiator, an outdoor heat exchanger provided outside the vehicle compartment for absorbing heat, and a control device the control device causing the radiator to dissipate at least the refrigerant discharged from the compressor
  • the air conditioning operation including the heating mode of heating the vehicle interior by absorbing heat with the outdoor heat exchanger is executed, and the control device stops the air conditioning operation in the heating mode
  • the outdoor heat exchanger is defrosted each time.
  • the air conditioner for a vehicle according to the second aspect of the present invention is the air conditioner for a vehicle according to the second aspect, wherein in the heating mode, the control device prevents malfunction if the state where the number of revolutions of the compressor is higher than the predetermined threshold continues for the first predetermined time t1. It is determined that the outdoor heat exchanger is defrosted after the air conditioning operation is stopped in the heating mode.
  • the malfunction preventing condition is It is determined that the condition is satisfied, and after the air conditioning operation is stopped in the heating mode, the outdoor heat exchanger is defrosted.
  • the control device in each of the inventions sets a predetermined defrost request flag when the heating mode is performed or when it is determined that the malfunction preventing condition is satisfied. If the air conditioning operation is performed in a mode other than the heating mode, the defrost request flag is reset, and after the air conditioning operation is stopped in a state where the defrost request flag is set, whether the outdoor heat exchanger can be defrosted If it is judged and permitted, the outdoor heat exchanger is defrosted, and a defrost request flag is reset.
  • the compressor is driven by the battery mounted on the vehicle, and the control device has no air conditioning requirement for the vehicle interior, and the battery is charging. It is characterized in that defrosting of the outdoor heat exchanger is permitted on condition that the remaining amount of the battery is equal to or more than a predetermined value.
  • the control device includes an air conditioning controller to which an air conditioning operation unit for performing an air conditioning setting operation in a vehicle compartment is connected; The air conditioning controller and the heat pump controller transmit and receive information via the vehicle communication bus, and the heat pump controller executes the heating mode, or the malfunction preventing condition is satisfied.
  • the defrost request flag is reset and the air conditioning operation is stopped in a state where the defrost request flag is set.
  • the outdoor heat is The defrosting of the converter is performed, the defrosting request flag is reset, and the air conditioning controller judges whether or not the outdoor heat exchanger can be defrosted when the defrosting request is received from the heat pump controller, and when permitting it, The defrosting permission of the outdoor heat exchanger is notified to the heat pump controller.
  • the air conditioner for a vehicle according to the invention of claim 7 is characterized in that in the above respective inventions, the control device defrosts the outdoor heat exchanger by heating the outdoor heat exchanger with a predetermined defroster. .
  • the compressor for compressing the refrigerant, the air flow passage through which the air supplied to the vehicle compartment flows, and the radiator for radiating the heat of the refrigerant and heating the air supplied from the air flow passage to the vehicle compartment And an outdoor heat exchanger provided outside the vehicle for absorbing heat of the refrigerant, and a control device, wherein the control device causes at least the refrigerant discharged from the compressor to be dissipated by the radiator and dissipated
  • the control device stops the air conditioning operation in the heating mode each time Since the outdoor heat exchanger is defrosted, defrosting of the outdoor heat exchanger is performed each time the air conditioning operation is stopped in the heating mode without judging the status of frost formation on the outdoor heat exchanger, etc.
  • the outdoor heat exchanger is defrosted, for example, the heating mode becomes extremely It is also possible to solve the inconvenience that the defrosting is started only after being performed for a short time. Further, as in the invention of claim 4, when the control device executes the heating mode or determines that the malfunction preventing condition is satisfied, a predetermined defrost request flag is set, and the air conditioning operation other than the heating mode is performed. If the defrost request flag is reset and the air conditioning operation is stopped while the defrost request flag is set, it is judged whether the outdoor heat exchanger can be defrosted or not, and it is permitted.
  • the compressor is driven by a battery mounted on the vehicle as in the invention of claim 5
  • the control device permits defrosting of the outdoor heat exchanger on the condition that there is no air conditioning request in the vehicle compartment and the battery is charging or the remaining amount of the battery is equal to or more than a predetermined value.
  • the control device comprises an air conditioning controller to which an air conditioning operation unit for performing an air conditioning setting operation in the vehicle compartment is connected, and a heat pump controller for controlling the operation of the compressor. If the controller and the heat pump controller transmit and receive information via the vehicle communication bus, if the heat pump controller executes the heating mode, or if it is determined that the malfunction preventing condition is satisfied, the defrost request is made. When the flag is set and the air conditioning operation is executed except for the heating mode, the defrost request flag is reset, and when the air conditioning operation is stopped in the state where the defrost request flag is set, the defrost for the air conditioning controller is performed.
  • the air conditioning controller determines whether the outdoor heat exchanger can be defrosted if the defrosting request is received from the heat pump controller, and if it permits, the defrosting permission of the outdoor heat exchanger is heat pump By notifying the controller, it is possible to appropriately prevent or suppress the decrease in the driving efficiency caused by the comfort of the vehicle interior and the frost formation of the outdoor heat exchanger.
  • the outdoor heat exchanger is heated by the predetermined defrosting apparatus as in the seventh aspect of the invention to defrost the outdoor heat exchanger. It will be able to reliably remove by melting.
  • FIG. 1 It is a block diagram of the air conditioning apparatus for vehicles of one Embodiment to which this invention is applied. It is a block diagram of the control apparatus of the air conditioning apparatus for vehicles of FIG. It is a schematic diagram of the airflow path of the air conditioning apparatus for vehicles of FIG. It is a control block diagram regarding compressor control in heating mode of the heat pump controller of FIG. It is a control block diagram regarding compressor control in the dehumidification heating mode of the heat pump controller of FIG. It is a control block diagram regarding the auxiliary heater (auxiliary heating device) control in the dehumidification heating mode of the heat pump controller of FIG. It is a flowchart explaining defrost control of the outdoor heat exchanger by the heat pump controller of FIG. It is a flowchart explaining another defrost control of the outdoor heat exchanger by the heat pump controller of FIG. It is a block diagram of the air conditioning apparatus for vehicles of the other Example of this invention.
  • FIG. 1 shows a configuration diagram of a vehicle air conditioner 1 according to an embodiment of the present invention.
  • the vehicle according to the embodiment to which the present invention is applied is an electric vehicle (EV) in which an engine (internal combustion engine) is not mounted, and is used for traveling with electric power charged in a battery 75 (FIG. 2) mounted in the vehicle.
  • the electric motor is driven to travel (not shown), and the vehicle air conditioner 1 of the present invention is also driven by the power of the battery 75.
  • the vehicle air conditioner 1 of the embodiment performs the air conditioning operation by the heat pump using the refrigerant circuit in the electric vehicle which can not be heated by the engine waste heat, and in this air conditioning operation, the heating mode, the dehumidifying heating mode, the dehumidifying cooling Each operation mode of the mode, the cooling mode, the MAX cooling mode (maximum cooling mode), and the auxiliary heater single mode is selectively executed.
  • the present invention is applicable not only to electric vehicles as vehicles, but also to so-called hybrid vehicles that use an engine and an electric motor for traveling, and is also applicable to ordinary vehicles traveling with an engine. Needless to say.
  • the vehicle air conditioner 1 of the embodiment performs air conditioning (heating, cooling, dehumidifying, and ventilating) of a vehicle compartment of an electric vehicle, and is an electric type that receives power from a battery 75 to drive and compress a refrigerant.
  • an outdoor expansion valve 6 pressure reducing device including a motor-operated valve for decompressing and expanding the refrigerant during heating, and a radiator 4 provided outside the vehicle for radiating heat during cooling
  • an indoor expansion valve 8 pressure reduction device including a motorized valve that decompresses and expands the refrigerant.
  • a heat sink 9 for cooling the air which absorbs heat from the outside of the vehicle interior by absorbing heat from the outside of the vehicle interior during cooling and dehumidification, the accumulator 12 and the like are sequentially connected by the refrigerant pipe 13, and the refrigerant circuit R is It is configured.
  • the refrigerant circuit R is filled with a predetermined amount of refrigerant and lubricating oil.
  • the outdoor heat exchanger 7 is provided with an outdoor fan 15. The outdoor fan 15 exchanges heat between the outdoor air and the refrigerant by forcibly ventilating the outdoor air to the outdoor heat exchanger 7, whereby the outdoor fan 15 is also outdoors when the vehicle is stopped (that is, the vehicle speed is 0 km / h).
  • the heat exchanger 7 is configured to ventilate outside air.
  • the outdoor heat exchanger 7 sequentially has the receiver dryer portion 14 and the subcooling portion 16 on the refrigerant downstream side, and the refrigerant pipe 13A that has come out of the outdoor heat exchanger 7 is a receiver via the solenoid valve 17 opened during cooling.
  • the refrigerant pipe 13B connected to the dryer unit 14 and at the outlet side of the subcooling unit 16 is connected to the inlet side of the heat absorber 9 via the indoor expansion valve 8.
  • the receiver dryer portion 14 and the subcooling portion 16 structurally constitute a part of the outdoor heat exchanger 7.
  • the refrigerant pipe 13B between the supercooling unit 16 and the indoor expansion valve 8 is provided in heat exchange relation with the refrigerant pipe 13C on the outlet side of the heat absorber 9, and both constitute an internal heat exchanger 19.
  • the refrigerant flowing into the indoor expansion valve 8 through the refrigerant pipe 13B is cooled (supercooled) by the low temperature refrigerant that has exited the heat absorber 9.
  • the refrigerant pipe 13A that has exited from the outdoor heat exchanger 7 is branched into the refrigerant pipe 13D, and the branched refrigerant pipe 13D is downstream of the internal heat exchanger 19 via the solenoid valve 21 opened during heating.
  • the refrigerant pipe 13C is connected to the accumulator 12, and the accumulator 12 is connected to the refrigerant suction side of the compressor 2.
  • the refrigerant pipe 13E on the outlet side of the radiator 4 is connected to the inlet side of the outdoor heat exchanger 7 via the outdoor expansion valve 6.
  • the refrigerant pipe 13G between the discharge side of the compressor 2 and the inlet side of the radiator 4 is provided with a solenoid valve 30 (constituting a flow path switching device) closed during dehumidifying heating and MAX cooling described later. There is.
  • the refrigerant pipe 13G is branched to a bypass pipe 35 on the upstream side of the solenoid valve 30, and the bypass pipe 35 is a solenoid valve 40 (also constituting a flow path switching device) opened during dehumidifying heating and MAX cooling. Is connected to the refrigerant pipe 13E on the downstream side of the outdoor expansion valve 6).
  • the bypass pipe 45, the solenoid valve 30, and the solenoid valve 40 constitute a bypass device 45.
  • the dehumidifying heating mode or MAX for directly flowing the refrigerant discharged from the compressor 2 into the outdoor heat exchanger 7 as described later It is possible to smoothly switch between the cooling mode and the heating mode, the dehumidifying cooling mode, and the cooling mode in which the refrigerant discharged from the compressor 2 flows into the radiator 4. Further, in the air flow passage 3 on the air upstream side of the heat absorber 9, suction ports for the outside air suction port and the inside air suction port are formed (represented by the suction port 25 in FIG.
  • this suction port A suction switching damper 26 is provided at 25 for switching the air introduced into the air flow passage 3 between the inside air (inside air circulation mode) that is the air inside the vehicle compartment and the outside air (outside air introduction mode) that is the air outside the vehicle outside There is. Further, on the air downstream side of the suction switching damper 26, an indoor blower (blower fan) 27 for supplying the introduced internal air and the external air to the air flow passage 3 is provided. Further, in FIG. 1, reference numeral 23 denotes an auxiliary heater as an auxiliary heating device provided in the vehicle air conditioner 1 of the embodiment.
  • the auxiliary heater 23 of the embodiment is constituted by a PTC heater which is an electric heater, and the inside of the air flow passage 3 which is on the windward side (air upstream side) of the radiator 4 with respect to the air flow of the air flow passage 3.
  • the auxiliary heater 23 is energized to generate heat, the air in the air flow passage 3 flowing into the radiator 4 through the heat absorber 9 is heated. That is, the auxiliary heater 23 serves as a so-called heater core to heat the vehicle interior or supplement it.
  • the air flow passage 3 on the downwind side (air downstream side) of the heat absorber 9 of the HVAC unit 10 is partitioned by the partition wall 10A, and a heating heat exchange passage 3A and a bypass passage 3B bypassing it are formed.
  • the radiator 4 and the auxiliary heater 23 described above are disposed in the heating heat exchange passage 3A.
  • the air (internal air and outside air) in the air flow passage 3 after flowing into the air flow passage 3 and passing through the heat absorber 9 is assisted.
  • An air mix damper 28 is provided to adjust the ratio of ventilation to the heating heat exchange passage 3A in which the heater 23 and the radiator 4 are disposed.
  • the HVAC unit 10 on the downwind side of the radiator 4 has a FOOT (foot) outlet 29A (first outlet) and a VENT (vent) outlet 29B (second outlet for the FOOT outlet 29A).
  • the FOOT blowout port 29A is a blowout port for blowing air under the foot of the vehicle compartment and is at the lowest position.
  • the VENT outlet 29B is an outlet for blowing air around the driver's chest and face in the vehicle compartment, and is above the FOOT outlet 29A.
  • the DEF outlet 29C is a outlet for blowing air to the inner surface of the windshield of the vehicle, and is located at the highest position above the other outlets 29A and 29B.
  • FIG. 2 shows a block diagram of the control device 11 of the vehicle air conditioner 1 of the embodiment.
  • the control device 11 is composed of an air conditioning controller 20 and a heat pump controller 32, each of which is constituted by a microcomputer which is an example of a computer having a processor, and these are CAN (Controller Area Network) and LIN (Local Interconnect Network).
  • the compressor 2 and the auxiliary heater 23 are also connected to the vehicle communication bus 65, and the air conditioning controller 20, the heat pump controller 32, the compressor 2 and the auxiliary heater 23 transmit and receive data via the vehicle communication bus 65. It is done.
  • the air conditioning controller 20 is a higher-level controller that controls the air conditioning inside the vehicle, and the outside air temperature sensor 33 for detecting the outside air temperature Tam of the vehicle and the outside air humidity for detecting the outside air humidity are input to the air conditioning controller 20.
  • a sensor 34 an HVAC suction temperature sensor 36 for detecting the temperature of the air (suctioned air temperature Tas) sucked into the air flow passage 3 from the suction port 25 and flowing into the heat absorber 9, the temperature of the air (internal air) in the vehicle compartment
  • An indoor air temperature sensor 37 for detecting (indoor temperature Tin)
  • an indoor air humidity sensor 38 for detecting the humidity of air in the vehicle compartment
  • an indoor CO 2 concentration sensor 39 for detecting carbon dioxide concentration in the vehicle compartment
  • a discharge pressure sensor 42 for detecting the discharge refrigerant pressure Pd of the compressor 2 and a solar radiation amount into the vehicle compartment.
  • the photo sensor type solar radiation sensor 51 the outputs of the vehicle speed sensor 52 for detecting the moving speed (vehicle speed) of the vehicle, and the air conditioning setting operation of the vehicle interior such as switching of the set temperature and the operation mode
  • An air conditioning operation unit (air conditioning operation unit) 53 for the purpose is connected.
  • the outdoor air blower 15, the indoor air blower (blower fan) 27, the suction switching damper 26, the air mix damper 28, and the air outlet dampers 31A to 31C are connected to the output of the air conditioning controller 20, and they are used for air conditioning It is controlled by the controller 20.
  • the battery 75 incorporates a controller, and the controller of the battery 75 transmits and receives data to and from the air conditioning controller 20 via the vehicle communication bus 65.
  • the heat pump controller 32 mainly controls the control of the refrigerant circuit R, and an input of the heat pump controller 32 is a discharge temperature sensor 43 for detecting a discharge refrigerant temperature Td of the compressor 2 and a suction refrigerant of the compressor 2
  • a suction pressure sensor 44 for detecting a pressure Ps, a suction temperature sensor 55 for detecting a suction refrigerant temperature Ts of the compressor 2, and a radiator temperature sensor 46 for detecting a refrigerant temperature (a radiator temperature TCI) of the radiator 4
  • a radiator pressure sensor 47 that detects the refrigerant pressure of the radiator 4 (radiator pressure PCI), a heat sink temperature sensor 48 that detects the refrigerant temperature (heat sink temperature Te) of the heat sink 9, and a refrigerant pressure of the heat sink 9
  • Heat sensor pressure sensor 49 for detecting the temperature, the auxiliary heater temperature sensor 50 for detecting the
  • the heat pump controller 32 outputs the outdoor expansion valve 6, the indoor expansion valve 8, the solenoid valve 30 (for reheating), the solenoid valve 17 (for cooling), the solenoid valve 21 (for heating), the solenoid valve 40 (bypass) ) Are connected, and they are controlled by the heat pump controller 32.
  • the compressor 2 and the auxiliary heater 23 each have a built-in controller, and the controller of the compressor 2 and the auxiliary heater 23 transmits / receives data to / from the heat pump controller 32 via the vehicle communication bus 65. It is controlled.
  • the heat pump controller 32 and the air conditioning controller 20 mutually transmit and receive data via the vehicle communication bus 65, and control each device based on the output of each sensor and the setting inputted by the air conditioning operation unit 53.
  • the operation of the vehicle air conditioner 1 of the embodiment having the above configuration will be described.
  • the controller 11 performs the air conditioning operation in the heating mode, the dehumidifying heating mode, the dehumidifying cooling mode, the cooling mode, the MAX cooling mode (maximum cooling mode) and the auxiliary heater. Switch between the operation modes in single mode and execute. First, an outline of the flow and control of the refrigerant in each operation mode will be described.
  • Heating mode When the heating mode is selected by the heat pump controller 32 (automatic mode) or by the manual air conditioning setting operation (manual mode) to the air conditioning operation unit 53, the heat pump controller 32 sets the solenoid valve 21 (for heating). Open and close the solenoid valve 17 (for cooling).
  • the solenoid valve 30 (for reheating) is opened, and the solenoid valve 40 (for bypass) is closed. Then, the compressor 2 is operated.
  • the air conditioning controller 20 operates the blowers 15 and 27, and the air mix damper 28 is basically blown out from the indoor blower 27 and passes through the heat absorber 9 and all the air in the air flow passage 3 is heated by the heat exchange passage 3A. In the state of ventilating to the auxiliary heater 23 and the radiator 4, the air volume may be adjusted. As a result, the high temperature and high pressure gas refrigerant discharged from the compressor 2 passes through the solenoid valve 30 and flows into the radiator 4 from the refrigerant pipe 13G.
  • the air in the air flow passage 3 is ventilated to the radiator 4, the air in the air flow passage 3 is a high temperature refrigerant in the heat radiator 4 (when the auxiliary heater 23 is operated, the auxiliary heater 23 and the radiator 4 are While the refrigerant in the radiator 4 loses its heat by air, is cooled, and condenses and liquefies.
  • the refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 through the refrigerant pipe 13E.
  • the refrigerant flowing into the outdoor expansion valve 6 is decompressed there, and then flows into the outdoor heat exchanger 7.
  • the refrigerant flowing into the outdoor heat exchanger 7 evaporates, and heat is pumped up from the outside air ventilated by the traveling or the outdoor blower 15. That is, the refrigerant circuit R is a heat pump. Then, the low temperature refrigerant leaving the outdoor heat exchanger 7 passes through the refrigerant piping 13A, the solenoid valve 21 and the refrigerant piping 13D, enters the accumulator 12 from the refrigerant piping 13C, and is separated into gas and liquid there, and then the gas refrigerant is the compressor 2 Repeat the cycle of sucking in Since the air heated by the radiator 4 (the auxiliary heater 23 and the radiator 4 when the auxiliary heater 23 operates) is blown out from the outlets 29A to 29C, this heats the vehicle interior.
  • the heat pump controller 32 calculates a target radiator pressure PCO (target value of the radiator pressure PCI) from the target heater temperature TCO (target value of the heating temperature TH described later) calculated by the air conditioning controller 20 from the target outlet temperature TAO.
  • the rotational speed NC of the compressor 2 is controlled based on the target radiator pressure PCO and the refrigerant pressure (radiator pressure PCI, high pressure of the refrigerant circuit R) detected by the radiator pressure sensor 47, and the radiator Control heating by 4. Further, the heat pump controller 32 opens the outdoor expansion valve 6 based on the refrigerant temperature (the radiator temperature TCI) of the radiator 4 detected by the radiator temperature sensor 46 and the radiator pressure PCI detected by the radiator pressure sensor 47.
  • the degree of subcooling SC of the refrigerant at the outlet of the radiator 4 is controlled.
  • the heat pump controller 32 compensates for the shortage by the heat generation of the auxiliary heater 23.
  • the energization of the auxiliary heater 23 is controlled. Thereby, comfortable heating of the vehicle interior is realized, and frost formation on the outdoor heat exchanger 7 is also suppressed.
  • the auxiliary heater 23 is disposed on the air upstream side of the radiator 4, the air flowing through the air flow passage 3 is ventilated to the auxiliary heater 23 in front of the radiator 4.
  • the auxiliary heater 23 when the auxiliary heater 23 is disposed on the air downstream side of the radiator 4, when the auxiliary heater 23 is configured by the PTC heater as in the embodiment, the temperature of the air flowing into the auxiliary heater 23 is the radiator Because the resistance value of the PTC heater increases and the current value also decreases and the calorific value decreases, the auxiliary heater 23 is disposed on the air upstream side of the radiator 4 in the embodiment. As described above, the capability of the auxiliary heater 23 composed of a PTC heater can be sufficiently exhibited. (2) Dehumidifying and Heating Mode Next, in the dehumidifying and heating mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valve 21.
  • the solenoid valve 30 is closed, the solenoid valve 40 is opened, and the degree of opening of the outdoor expansion valve 6 is fully closed. Then, the compressor 2 is operated.
  • the air conditioning controller 20 operates the blowers 15 and 27, and the air mix damper 28 is basically blown out from the indoor blower 27 and passes through the heat absorber 9 and all the air in the air flow passage 3 is heated by the heat exchange passage 3A. In the state of ventilating to the auxiliary heater 23 and the radiator 4, the air volume is also adjusted.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 2 to the refrigerant pipe 13G flows into the bypass pipe 35 without going to the radiator 4, and passes through the solenoid valve 40 and the refrigerant pipe on the downstream side of the outdoor expansion valve 6 It will reach 13E.
  • the outdoor expansion valve 6 since the outdoor expansion valve 6 is fully closed, the refrigerant flows into the outdoor heat exchanger 7.
  • the refrigerant flowing into the outdoor heat exchanger 7 is air-cooled and condensed by traveling there or by the outside air ventilated by the outdoor blower 15.
  • the refrigerant leaving the outdoor heat exchanger 7 flows from the refrigerant pipe 13A through the solenoid valve 17 into the receiver dryer portion 14 and the supercooling portion 16 sequentially.
  • the refrigerant is subcooled.
  • the refrigerant leaving the subcooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13B, passes through the internal heat exchanger 19, and reaches the indoor expansion valve 8.
  • the refrigerant After the refrigerant is depressurized by the indoor expansion valve 8, the refrigerant flows into the heat absorber 9 and evaporates.
  • the air blown out from the indoor blower 27 is cooled by the heat absorption action, and the moisture in the air condenses and adheres to the heat absorber 9, so the air in the air flow passage 3 is cooled, and Dehumidified.
  • the refrigerant evaporated by the heat absorber 9 passes through the internal heat exchanger 19 and reaches the accumulator 12 via the refrigerant pipe 13C, and the circulation through which the refrigerant is sucked into the compressor 2 is repeated.
  • the valve opening degree of the outdoor expansion valve 6 is fully closed, it is possible to suppress or prevent the disadvantage that the refrigerant discharged from the compressor 2 flows back from the outdoor expansion valve 6 into the radiator 4 It becomes.
  • the heat pump controller 32 supplies power to the auxiliary heater 23 to generate heat.
  • the heat pump controller 32 is a compressor based on the temperature of the heat absorber 9 detected by the heat absorber temperature sensor 48 (heat absorber temperature Te) and the target heat absorber temperature TEO which is a target value of the heat absorber temperature Te calculated by the air conditioning controller 20.
  • the heat absorber is controlled by controlling the rotation speed NC of 2 and controlling the energization (heating due to heat generation) of the auxiliary heater 23 based on the auxiliary heater temperature Tptc detected by the auxiliary heater temperature sensor 50 and the target heater temperature TCO described above.
  • the temperature of the air blown into the vehicle compartment from each of the outlets 29A to 29C by the heating by the auxiliary heater 23 is properly prevented.
  • the auxiliary heater 23 is disposed on the air upstream side of the radiator 4, the air heated by the auxiliary heater 23 passes through the radiator 4, but in this dehumidifying and heating mode, the refrigerant 4 Since the air is not flowed, the problem that the radiator 4 absorbs heat from the air heated by the auxiliary heater 23 is also eliminated.
  • the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valve 21. Also, the solenoid valve 30 is opened and the solenoid valve 40 is closed. Then, the compressor 2 is operated.
  • the air conditioning controller 20 operates the blowers 15 and 27, and the air mix damper 28 is basically blown out from the indoor blower 27 and passes through the heat absorber 9 and all the air in the air flow passage 3 is heated by the heat exchange passage 3A. In the state of ventilating to the auxiliary heater 23 and the radiator 4, the air volume is also adjusted.
  • the high temperature and high pressure gas refrigerant discharged from the compressor 2 passes through the solenoid valve 30 and flows into the radiator 4 from the refrigerant pipe 13G. Since the air in the air flow passage 3 is ventilated to the radiator 4, the air in the air flow passage 3 is heated by the high temperature refrigerant in the radiator 4, while the refrigerant in the radiator 4 heats the air. It is taken away, cooled, and condensed and liquefied. The refrigerant leaving the radiator 4 passes through the refrigerant pipe 13E to reach the outdoor expansion valve 6, and then flows into the outdoor heat exchanger 7 through the outdoor expansion valve 6 which is controlled to be open.
  • the refrigerant flowing into the outdoor heat exchanger 7 is air-cooled and condensed by traveling there or by the outside air ventilated by the outdoor blower 15.
  • the refrigerant leaving the outdoor heat exchanger 7 flows from the refrigerant pipe 13A through the solenoid valve 17 into the receiver dryer portion 14 and the supercooling portion 16 sequentially.
  • the refrigerant is subcooled.
  • the refrigerant leaving the subcooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13B, passes through the internal heat exchanger 19, and reaches the indoor expansion valve 8. After the refrigerant is depressurized by the indoor expansion valve 8, the refrigerant flows into the heat absorber 9 and evaporates.
  • the moisture in the air blown out from the indoor blower 27 condenses and adheres to the heat sink 9, so that the air is cooled and dehumidified.
  • the refrigerant evaporated by the heat absorber 9 passes through the internal heat exchanger 19 and reaches the accumulator 12 via the refrigerant pipe 13C, and the circulation through which the refrigerant is sucked into the compressor 2 is repeated.
  • the heat pump controller 32 does not energize the auxiliary heater 23, so the air cooled by the heat absorber 9 and dehumidified air passes through the radiator 4 and is reheated (heat radiation capacity is lower than that during heating) Be done. As a result, dehumidifying and cooling of the passenger compartment is performed.
  • the heat pump controller 32 detects the temperature of the heat absorber 9 (heat absorber temperature Te) detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO (sent from the air conditioning controller 20) as its target value. Control the rotational speed NC. Further, the heat pump controller 32 calculates the target radiator pressure PCO from the target heater temperature TCO described above, and the target radiator pressure PCO and the refrigerant pressure of the radiator 4 detected by the radiator pressure sensor 47 (the radiator pressure PCI. The valve opening degree of the outdoor expansion valve 6 is controlled based on the high pressure of the refrigerant circuit R, and the heating by the radiator 4 is controlled.
  • the heat pump controller 32 fully opens the degree of the outdoor expansion valve 6 in the dehumidifying cooling mode. Then, the compressor 2 is operated and the auxiliary heater 23 is not energized.
  • the air conditioning controller 20 operates the blowers 15, 27.
  • the air mix damper 28 is blown out from the indoor blower 27 and the air in the air flow passage 3 which has passed through the heat absorber 9 is the auxiliary heater 23 of the heating heat exchange passage 3A. And let it be in the state which adjusts the ratio ventilated to the radiator 4.
  • the high temperature / high pressure gas refrigerant discharged from the compressor 2 flows from the refrigerant pipe 13G to the radiator 4 through the solenoid valve 30, and the refrigerant leaving the radiator 4 passes through the refrigerant pipe 13E to the outdoor expansion valve 6 Lead to At this time, since the outdoor expansion valve 6 is fully opened, the refrigerant passes through it and flows into the outdoor heat exchanger 7 where it is cooled by air or by the outside air ventilated by the outdoor blower 15 by running. Liquefy.
  • the refrigerant leaving the outdoor heat exchanger 7 flows from the refrigerant pipe 13A through the solenoid valve 17 into the receiver dryer portion 14 and the supercooling portion 16 sequentially. Here, the refrigerant is subcooled.
  • the refrigerant leaving the subcooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13B, passes through the internal heat exchanger 19, and reaches the indoor expansion valve 8. After the refrigerant is depressurized by the indoor expansion valve 8, the refrigerant flows into the heat absorber 9 and evaporates. The air blown out from the indoor blower 27 is cooled by the heat absorption action at this time. Further, the moisture in the air condenses and adheres to the heat absorber 9. The refrigerant evaporated by the heat absorber 9 passes through the internal heat exchanger 19 and reaches the accumulator 12 via the refrigerant pipe 13C, and the circulation through which the refrigerant is sucked into the compressor 2 is repeated.
  • the air cooled by the heat absorber 9 and dehumidified is blown out from the blowout ports 29A to 29C into the vehicle compartment (a part of the air passes through the radiator 4 for heat exchange). It will be done. Further, in the cooling mode, the heat pump controller 32 generates the compressor 2 based on the temperature (heat absorber temperature Te) of the heat absorber 9 detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO described above, which is its target value. Control the number of revolutions NC. (5) MAX cooling mode (maximum cooling mode) Next, in the MAX cooling mode as the maximum cooling mode, the heat pump controller 32 opens the solenoid valve 17 and closes the solenoid valve 21.
  • the solenoid valve 30 is closed, the solenoid valve 40 is opened, and the degree of opening of the outdoor expansion valve 6 is fully closed. Then, the compressor 2 is operated and the auxiliary heater 23 is not energized.
  • the air conditioning controller 20 operates the blowers 15 and 27, and the air mix damper 28 is blown out from the indoor blower 27 and the air in the air flow passage 3 having passed through the heat absorber 9 is an auxiliary heater of the heating heat exchange passage 3A. 23 and the radiator 4 are adjusted.
  • the high-temperature, high-pressure gas refrigerant discharged from the compressor 2 to the refrigerant pipe 13G flows into the bypass pipe 35 without going to the radiator 4, and passes through the solenoid valve 40 and the refrigerant pipe on the downstream side of the outdoor expansion valve 6 It will reach 13E.
  • the outdoor expansion valve 6 since the outdoor expansion valve 6 is fully closed, the refrigerant flows into the outdoor heat exchanger 7.
  • the refrigerant flowing into the outdoor heat exchanger 7 is air-cooled and condensed by traveling there or by the outside air ventilated by the outdoor blower 15.
  • the refrigerant leaving the outdoor heat exchanger 7 flows from the refrigerant pipe 13A through the solenoid valve 17 into the receiver dryer portion 14 and the supercooling portion 16 sequentially.
  • the refrigerant is subcooled.
  • the refrigerant leaving the subcooling section 16 of the outdoor heat exchanger 7 enters the refrigerant pipe 13B, passes through the internal heat exchanger 19, and reaches the indoor expansion valve 8.
  • the refrigerant After the refrigerant is depressurized by the indoor expansion valve 8, the refrigerant flows into the heat absorber 9 and evaporates.
  • the air blown out from the indoor blower 27 is cooled by the heat absorption action at this time. Further, since the moisture in the air condenses and adheres to the heat absorber 9, the air in the air flow passage 3 is dehumidified.
  • the refrigerant evaporated by the heat absorber 9 passes through the internal heat exchanger 19 and reaches the accumulator 12 via the refrigerant pipe 13C, and the circulation through which the refrigerant is sucked into the compressor 2 is repeated.
  • the outdoor expansion valve 6 since the outdoor expansion valve 6 is fully closed, it is possible to similarly suppress or prevent the problem that the refrigerant discharged from the compressor 2 flows back from the outdoor expansion valve 6 into the radiator 4 . As a result, it is possible to suppress or eliminate the decrease in the refrigerant circulation amount and secure the air conditioning capacity.
  • the heat pump controller 32 generates a compressor based on the temperature (heat absorber temperature Te) of the heat absorber 9 detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO described above, which is its target value. Control the rotation speed NC of 2.
  • the controller 11 of the embodiment stops the compressor 2 of the refrigerant circuit R and the outdoor blower 15 when excessive frost formation occurs in the outdoor heat exchanger 7, etc., and the auxiliary heater In the auxiliary heater only mode, it is possible to energize the vehicle 23 and heat the vehicle interior only with the auxiliary heater 23.
  • the heat pump controller 32 controls the energization (heat generation) of the auxiliary heater 23 based on the auxiliary heater temperature Tptc detected by the auxiliary heater temperature sensor 50 and the target heater temperature TCO described above.
  • the air conditioning controller 20 operates the indoor fan 27, and the air mix damper 28 ventilates the air in the air flow path 3 blown out from the indoor fan 27 to the auxiliary heater 23 of the heating heat exchange path 3A to obtain the air volume. It will be in the state to adjust. Since the air heated by the auxiliary heater 23 is blown out into the vehicle compartment from the air outlets 29A to 29C, this heats the vehicle interior.
  • the air conditioning controller 20 calculates the above-mentioned target blowing temperature TAO from the following formula (I).
  • the target blowing temperature TAO is a target value of the temperature of air blown out into the vehicle compartment.
  • TAO (Tset ⁇ Tin) ⁇ K + Tbal (f (Tset, SUN, Tam)) (I)
  • Tset is the set temperature of the vehicle interior set by the air conditioning operation unit 53
  • Tin is the indoor temperature detected by the inside air temperature sensor 37
  • K is a coefficient
  • Tbal is the set temperature Tset
  • the amount of solar radiation detected by the solar radiation sensor 51 SUN it is a balance value calculated from the outside air temperature Tam detected by the outside air temperature sensor 33.
  • the target blowing temperature TAO is higher as the outside air temperature Tam is lower, and decreases as the outside air temperature Tam increases.
  • the heat pump controller 32 selects one of the above operation modes based on the outside air temperature Tam (detected by the outside air temperature sensor 33) transmitted from the air conditioning controller 20 via the vehicle communication bus 65 at the time of startup and the target blowout temperature TAO. The operation mode is selected, and each operation mode is transmitted to the air conditioning controller 20 via the vehicle communication bus 65.
  • the outside air temperature Tam After startup, the outside air temperature Tam, the humidity inside the vehicle compartment, the target air outlet temperature TAO, the heating temperature TH (the temperature of the air on the downwind side of the radiator 4; estimated value), the target heater temperature TCO, the heat sink temperature Te,
  • heating mode, dehumidification heating mode, dehumidification can be properly performed according to environmental conditions and necessity of dehumidification
  • the cooling mode, the cooling mode, the MAX cooling mode, and the auxiliary heater single mode to control the temperature of the air blown into the vehicle compartment to the target blowing temperature TAO, a comfortable and efficient vehicle interior air conditioning is realized.
  • FIG. 4 is a control block diagram of the heat pump controller 32 for determining the target rotational speed (compressor target rotational speed) TGNCh of the compressor 2 for the heating mode.
  • the target subcooling degree TGSC which is the target value of the subcooling degree SC at the outlet of the radiator 4, and the target heater temperature TCO described above, which is the target value of the heating temperature TH.
  • the F / F operation amount TGNChff of the compressor target rotational speed is calculated based on the target radiator pressure PCO which is a target value of the pressure of the radiator 4 (transmitted from the air conditioning controller 20).
  • the above-mentioned TH for calculating the air volume ratio SW is the temperature of air on the leeward side of the radiator 4 (hereinafter referred to as a heating temperature), and the heat pump controller 32 calculates the first-order lag calculation formula (II) below. presume.
  • TH (INTL ⁇ TH0 + Tau ⁇ THz) / (Tau + INTL) ⁇ (II)
  • INTL is a calculation cycle (constant)
  • Tau is a first-order lag time constant
  • TH0 is a steady-state value of the heating temperature TH in a steady state before the first-order lag calculation
  • THz is a previous value of the heating temperature TH.
  • the heating temperature TH is transmitted to the air conditioning controller 20 via the vehicle communication bus 65.
  • the target radiator pressure PCO is calculated by the target value calculator 59 based on the target degree of supercooling TGSC and the target heater temperature TCO.
  • the F / B (feedback) manipulated variable computing unit 60 computes the F / B manipulated variable TGNChfb of the compressor target rotational speed based on the target radiator pressure PCO and the radiator pressure PCI which is the refrigerant pressure of the radiator 4 Do.
  • the F / F manipulated variable TGNCnff computed by the F / F manipulated variable computing unit 58 and TGNChfb computed by the F / B manipulated variable computing unit 60 are added by the adder 61, and the limit setting unit 62 sets the control upper limit value ECNpdLimHi After the control lower limit value ECNpdLimLo is limited, it is determined as the compressor target rotation speed TGNCh.
  • the heat pump controller 32 controls the rotation speed NC of the compressor 2 based on the compressor target rotation speed TGNCh. (9) Control of the compressor 2 and the auxiliary heater 23 in the dehumidifying and heating mode by the heat pump controller 32 On the other hand, FIG.
  • FIG. 6 is a control block diagram of the heat pump controller 32.
  • the F / F operation amount calculation unit 63 of the heat pump controller 32 is a target heat radiation that is a target value of the outside air temperature Tam, the volumetric air flow rate Ga of the air flowing into the air flow passage 3, and the pressure of the radiator 4 (radiator pressure PCI).
  • the F / F manipulated variable TGNCcff of the compressor target rotational speed is calculated based on the target pressure T.sub.o of the heat sink 9 and the target heat sink temperature T.sub.oO which is the target value of the temperature of the heat sink 9 (the heat sink temperature Te).
  • the F / B manipulated variable computing unit 64 computes the F / B manipulated variable TGNCcfb of the compressor target rotational speed based on the target heat absorber temperature TEO (transmitted from the air conditioning controller 20) and the heat absorber temperature Te.
  • the F / F operation amount TGNCcff calculated by the F / F operation amount calculation unit 63 and the F / B operation amount TGNCcfb calculated by the F / B operation amount calculation unit 64 are added by the adder 66 and the limit setting unit 67 After the control upper limit value TGNCcLimHi and the control lower limit value TGNCcLimLo are limited, the compressor target rotational speed TGNCc is determined.
  • the heat pump controller 32 controls the rotation speed NC of the compressor 2 based on the compressor target rotation speed TGNCc.
  • FIG. 6 is a control block diagram of the heat pump controller 32 for determining the auxiliary heater request capacity TGQPTC of the auxiliary heater 23 in the dehumidifying and heating mode.
  • the target heater temperature TCO and the auxiliary heater temperature Tptc are input to the subtractor 73 of the heat pump controller 32, and the deviation (TCO-Tptc) of the target heater temperature TCO and the auxiliary heater temperature Tptc is calculated.
  • the deviation (TCO-Tptc) is input to the F / B control unit 74, and the F / B control unit 74 eliminates the deviation (TCO-Tptc) and the auxiliary heater temperature Tptc becomes the target heater temperature TCO. Calculate the required ability F / B operation amount.
  • the auxiliary heater required capacity F / B manipulated variable Qafb calculated by the F / B control unit 74 is limited by the limit setting unit 76 with the control upper limit value QptcLimHi and the control lower limit value QptcLimLo as an auxiliary heater required capacity TGQPTC. It is determined.
  • the controller 32 controls the energization of the auxiliary heater 23 based on the auxiliary heater request capability TGQPTC to generate (heat) the auxiliary heater 23 so that the auxiliary heater temperature Tptc becomes the target heater temperature TCO. Control.
  • the heat pump controller 32 controls the operation of the compressor based on the heat absorber temperature Te and the target heat absorber temperature TEO, and controls the heat generation of the auxiliary heater 23 based on the target heater temperature TCO.
  • the cooling and the dehumidification by the heat absorber 9 in the dehumidifying and heating mode, and the heating by the auxiliary heater 23 are properly controlled.
  • the air conditioning controller 20 The air mix damper 28 is controlled to adjust the amount of ventilation to the radiator 4 (and the auxiliary heater 23).
  • SW (TAO-Te) / (TH-Te) ⁇ ⁇ (III) That is, the air volume ratio SW ventilated to the radiator 4 and the auxiliary heater 23 of the heating heat exchange passage 3A changes in the range of 0 ⁇ SW ⁇ 1, and “0” does not ventilate the heating heat exchange passage 3A.
  • the heat pump controller 32 performs the defrosting control of the outdoor heat exchanger 7 as follows. (11-1) Defrosting control of the outdoor heat exchanger 7 (part 1) Next, an example of the defrosting control of the outdoor heat exchanger 7 will be described using FIG. 7.
  • the heat pump controller 32 first determines whether the vehicle has been activated in step S1 of FIG. 7 and an air conditioning request for the passenger compartment (hereinafter referred to as an HP air conditioning request) by the air conditioning device 1 for a vehicle. Determine if it is. In this case, it is determined from the ON information (sent from the air conditioning controller 20) of the ignition (IG) whether or not the vehicle is activated.
  • the HP air conditioning request is an operation request for the air conditioning system 1 for a vehicle, and in the embodiment, the ON / OFF switch of the air conditioner provided in the air conditioning operation unit 53 is turned ON whether or not there is the HP air conditioning request. It judges from the information (it transmitted from the air conditioning controller 20) of whether it was. Then, when the vehicle is started and the HP air conditioning request is made, the heat pump controller 32 starts the air conditioning operation by the air conditioning device 1 for a vehicle, and proceeds to step S2. On the other hand, if step S1 fails, the process proceeds to step S6.
  • step S6 the heat pump controller 32 determines whether or not there is an HP air conditioning request, and if there is an HP air conditioning request, that is, if there is an HP air conditioning request regardless of whether the vehicle is activated or not.
  • the air conditioning operation by the air conditioner 1 is started, and the process proceeds to step S2.
  • step S6 the air conditioning operation by the vehicle air conditioner 1 is stopped, and the process proceeds to step S7.
  • step S2 the heat pump controller 32 determines whether or not the vehicle air conditioner 1 (HP) is determined to have a failure. If the failure is not determined, the process proceeds to step S3 and the current operation mode is the heating mode to decide.
  • step S4 the defrost request flag fDFSTReq is set ("1"). If it is determined in step S3 that the current operation mode is other than the heating mode, the process proceeds to step S5, and the defrost request flag fDFSTReq is reset ("0"). Further, the heat pump controller 32 is provided with a non-volatile memory (EEP-ROM) 80, and the state of the defrost request flag fDFSTReq set (“1”) and reset (“0”) is stored in the non-volatile memory 80.
  • EEP-ROM non-volatile memory
  • step S7 determines whether the defrost request flag fDFSTReq is set (“1”), and if reset (“0”), proceeds to step S12, and the non-volatile memory 80
  • the state of the defrost request flag fDFSTReq held in is kept as the previous state (previous value).
  • step S4 the heat pump controller 32 sets the defrost request flag fDFSTReq ("1"). Is notified to the air conditioning controller 20 as a defrost request (FIG. 2).
  • the heat pump controller 32 proceeds from step S7 to step S8, and determines whether the defrosting permission has been notified from the air conditioning controller 20 or not.
  • the air conditioning controller 20 is notified that the defrosting request flag fDFSTReq is set as the defrosting request from the heat pump controller 32 as described above
  • the current state of the vehicle is the defrosting permission of the outdoor heat exchanger 7 Whether the defrosting of the outdoor heat exchanger 7 is possible or not is judged by judging whether the conditions are satisfied.
  • the defrost permission condition in the case of the embodiment is that there is no HP air conditioning request described above, and the battery 75 is being charged (the vehicle is stopped) or the remaining amount of the battery 75 is equal to or more than a predetermined value.
  • the air conditioning controller 20 sets ("1") the defrosting permission flag fDFSTPerm.
  • the fact that the defrosting permission flag fDFSTPerm is set ("1") is notified from the air-conditioning controller 20 to the heat pump controller 32 as the defrosting permission (FIG. 2).
  • the heat pump controller 32 proceeds from step S8 to step S9 to perform the defrosting operation of the outdoor heat exchanger 7 when notified of the defrosting permission from the air conditioning controller 20, and proceeds to step S12 when not notified.
  • the heat pump controller 32 sets the refrigerant circuit R to the heating mode state in the defrosting operation in step S9, then fully opens the outdoor expansion valve 6 and sets the air volume ratio SW by the air mix damper 28 to "0". It is set as the state which does not ventilate to the heat exchange path 3A for heating (it does not ventilate to the radiator 4). Then, the compressor 2 is operated, and the high temperature refrigerant discharged from the compressor 2 flows through the radiator 4 and the outdoor expansion valve 6 into the outdoor heat exchanger 7 to heat the outdoor heat exchanger 7. Thereby, the frost formation of the outdoor heat exchanger 7 is melted.
  • the compressor 2, the outdoor expansion valve 6, and the high temperature refrigerant discharged from the compressor 2 constitute the defrosting device of the outdoor heat exchanger 7 in the present invention.
  • a predetermined electric heater for example, in the case of a vehicle equipped with an engine, a circulation circuit of engine cooling water etc. is installed as a defroster, and the outdoor heat exchanger 7 is It may heat and defrost.
  • step S10 the heat pump controller 32 determines that the temperature of the outdoor heat exchanger 7 (in this case, the outdoor heat exchanger temperature TXO) detected by the outdoor heat exchanger temperature sensor 54 is a predetermined defrost end temperature (for example, + 3 ° C., etc.) It is judged whether the higher state continues for a predetermined time (for example, several minutes) (defrost completion condition), and defrost of the outdoor heat exchanger 7 is finished and the outdoor heat exchanger temperature TXO is If the defrost termination condition is satisfied, the process proceeds to step S11, and it is determined that the defrost is completed, and the above-described defrost request flag fDFSTReq is reset ("0") (step S7 to step S12 is defrost control).
  • the defrost completion condition for example, several minutes
  • the heat pump controller 32 performs the air conditioning operation in the heating mode if the defrost permission notification is received from the air conditioning controller 20 without judging the frost formation condition on the outdoor heat exchanger 7 or the like.
  • the outdoor heat exchanger 7 is defrosted each time it is stopped.
  • FIG. 8 shows another example of the defrosting control of the outdoor heat exchanger 7.
  • the steps denoted by the same reference numerals as those in FIG. 7 are the same as in FIG. In the control example of FIG.
  • the heat pump controller 32 determines in step S3 whether the current operation mode is the heating mode, and if the current operation mode is the heating mode, the malfunction determination is performed in steps S13 and S14. That is, when the current operation mode is the heating mode in step S3, the heat pump controller 32 proceeds to step S13 and determines whether the first malfunction preventing condition is satisfied.
  • a predetermined threshold for example, 3000 rpm
  • the first predetermined time t1 for example, 5 minutes
  • the heat pump controller 32 performs the first malfunction when the operation with the number of revolutions of the compressor 2 being higher than the threshold continues for the first predetermined time t1. It is determined that the prevention condition is established, and the process proceeds from step S13 to step S4, and the defrost request flag fDFSTReq is set ("1"). On the other hand, if the first malfunction prevention condition is not satisfied in step S13, the heat pump controller 32 proceeds to step S14 to determine whether the second malfunction prevention condition is satisfied this time.
  • the second malfunction prevention condition of the embodiment is whether or not the air conditioning operation in the heating mode has continued for a second predetermined time t2 (for example, 10 minutes) longer than the first predetermined time t1.
  • the heat pump controller 32 determines that the second malfunction prevention condition is satisfied, and proceeds from step S14 to step S4, and requests defrosting The flag fDFSTReq is set ("1").
  • the heat pump controller 32 proceeds to step S5 and resets the defrosting request flag fDFSTReq (“0”).
  • Other control is the same as in the case of FIG. In the control example in this case, even if the heating mode is performed, the defrost request flag fDFSTReq is not set if the first and second malfunction prevention conditions are not satisfied, so the air conditioning operation unit 53 is erroneously operated.
  • the heat pump controller 32 performs defrosting of the outdoor heat exchanger 7 every time the air conditioning operation is stopped in the heating mode. Each time the air conditioning operation is stopped in the heating mode, defrosting of the outdoor heat exchanger 7 is performed without determining the state of frost formation and the like. As a result, it is possible to prevent or suppress the decrease in the operating efficiency associated with the frost formation on the outdoor heat exchanger 7 with a relatively simple control.
  • the defrosting of the outdoor heat exchanger 7 is performed after the air conditioning operation is stopped, it is possible to prevent or suppress the decrease in the comfort of the vehicle interior.
  • the first malfunction prevention condition is satisfied.
  • the outdoor heat exchanger 7 is defrosted, or the heating mode is continuously performed for a second predetermined time t2 longer than the first predetermined time t1. In this case, it is determined that the second malfunction prevention condition is satisfied, and after the air conditioning operation is stopped in the heating mode, defrosting of the outdoor heat exchanger 7 is performed.
  • the heating mode is extremely short. It is also possible to eliminate the inconvenience that, for example, defrosting of the outdoor heat exchanger 7 is started only when time is taken.
  • the defrost request flag fDFSTReq is set ("1").
  • the defrost request flag fDFSTReq is reset ("0") and the air conditioning operation is stopped in a state where the defrost request flag fDFSTReq is set ("1").
  • the outdoor heat exchanger 7 After that, it is judged whether the outdoor heat exchanger 7 is defrostable or not, and if permitted, the outdoor heat exchanger 7 is defrosted and the defrost request flag fDFSTReq is reset ("0"). Therefore, when the compressor 2 is driven by the battery 75 mounted on the vehicle as in the embodiment, the air conditioning controller 20 has no request for air conditioning in the vehicle compartment. Also, by allowing defrosting of the outdoor heat exchanger 7 under the condition that the battery 75 is being charged or the remaining amount of the battery 75 is equal to or more than a predetermined value, the traveling of the vehicle is adversely affected. The outdoor heat exchanger 7 can be appropriately defrosted without having to do so.
  • the defrost request flag fDFSTReq is reset ("0"). Therefore, when the air conditioning operation is stopped in a mode other than the heating mode, defrosting of the outdoor heat exchanger 7 is performed.
  • control device 11 is configured of the air conditioning controller 20 to which the air conditioning operation unit 53 for performing the air conditioning setting operation of the vehicle compartment is connected, and the heat pump controller 32 for controlling the operation of the compressor 2;
  • the heat pump controller 32 executes the heating mode, or the first or second
  • the defrost request flag fDFSTReq is set (“1”)
  • the defrost request flag fDFSTReq is reset (“0”)
  • the air conditioning operation is stopped with the defrost request flag fDFSTReq set (“1”)
  • the outdoor heat exchanger 7 is defrosted, and the defrost request flag fDFSTReq is
  • the air conditioner controller 20 determines whether the outdoor heat exchanger 7 can be defrosted or not, and when permitting it, the defrosting permission of the outdoor heat exchanger 7 is By notifying the controller 32, it is possible to appropriately prevent or suppress the comfort in the vehicle interior and the decrease in the operating efficiency caused by the frost formation on the outdoor heat exchanger 7. Then, in the embodiment, the outdoor heat exchanger 7 is heated by the defrosting apparatus such as high temperature refrigerant discharged from the compressor 2 and the outdoor heat exchanger 7 is defrosted, so the outdoor heat exchanger 7 is It will be possible to melt and remove the frost formation reliably.
  • the defrosting apparatus such as high temperature refrigerant discharged from the compressor 2 and the outdoor heat exchanger 7 is defrosted
  • FIG. 9 shows a configuration diagram of a vehicle air conditioner 1 of another embodiment to which the present invention is applied.
  • the same reference numerals as in FIG. 1 have the same or similar functions.
  • the outlet of the supercooling unit 16 is connected to the check valve 18, and the outlet of the check valve 18 is connected to the refrigerant pipe 13B.
  • the refrigerant pipe 13B (indoor expansion valve 8) side is in the forward direction.
  • the refrigerant pipe 13E on the outlet side of the radiator 4 is branched in front of the outdoor expansion valve 6, and the branched refrigerant pipe (hereinafter referred to as a second bypass pipe) 13F is a solenoid valve 22 (for dehumidification) Is connected in communication with the refrigerant pipe 13B on the downstream side of the check valve 18.
  • an evaporation pressure adjusting valve 70 is connected to the refrigerant pipe 13C on the outlet side of the heat absorber 9 on the refrigerant downstream side of the internal heat exchanger 19 and on the refrigerant upstream side from the junction with the refrigerant pipe 13D. .
  • the solenoid valve 22 and the evaporation pressure regulating valve 70 are also connected to the output of the heat pump controller 32.
  • the bypass pipe 45, the solenoid valve 30, and the bypass device 45 including the solenoid valve 40 in FIG. 1 of the embodiment described above are not provided.
  • the other parts are the same as those in FIG.
  • the operation of the vehicle air conditioner 1 of this embodiment will be described with the above configuration.
  • the heat pump controller 32 switches and executes each operation mode of heating mode, dehumidifying heating mode, internal cycle mode, dehumidifying cooling mode, cooling mode and auxiliary heater single mode in the air conditioning operation of this embodiment (MAX cooling mode is implemented Not present in the example).
  • the solenoid valve 22 is closed in the heating mode (including defrosting) and in the dehumidifying / cooling mode and the cooling mode.
  • the heat pump controller 32 opens the solenoid valve 21 (for heating) in this embodiment, and the solenoid valve 17 ( Close for cooling.
  • the solenoid valve 22 (for dehumidification) is opened. Then, the compressor 2 is operated.
  • the air conditioning controller 20 operates the blowers 15 and 27, and the air mix damper 28 is basically blown out from the indoor blower 27 and passes through the heat absorber 9 and all the air in the air flow passage 3 is heated by the heat exchange passage 3A. In the state of ventilating to the auxiliary heater 23 and the radiator 4, the air volume is also adjusted. As a result, the high-temperature, high-pressure gas refrigerant discharged from the compressor 2 flows into the radiator 4 from the refrigerant pipe 13G.
  • the air in the air flow passage 3 which has flowed into the heating heat exchange passage 3A is ventilated in the radiator 4, the air in the air flow passage 3 is heated by the high temperature refrigerant in the radiator 4, while the radiator is The refrigerant in 4 is cooled by the heat taken by the air and condenses and liquefies.
  • the refrigerant liquefied in the radiator 4 exits the radiator 4 and then reaches the outdoor expansion valve 6 through the refrigerant pipe 13E.
  • the refrigerant flowing into the outdoor expansion valve 6 is decompressed there, and then flows into the outdoor heat exchanger 7.
  • the refrigerant flowing into the outdoor heat exchanger 7 evaporates, and heat is pumped up from the outside air ventilated by the traveling or the outdoor blower 15.
  • the refrigerant circuit R is a heat pump. Then, the low temperature refrigerant leaving the outdoor heat exchanger 7 passes through the refrigerant pipe 13A, the solenoid valve 21 and the refrigerant pipe 13D, enters the accumulator 12 from the refrigerant pipe 13C, and is gas-liquid separated there, and then the gas refrigerant is the compressor 2 Repeat the cycle of sucking in Further, a part of the condensed refrigerant flowing through the refrigerant pipe 13E through the radiator 4 is diverted, and passes through the solenoid valve 22 to the indoor expansion valve 8 through the internal heat exchanger 19 from the second bypass pipe 13F and the refrigerant pipe 13B. It will be.
  • the refrigerant After the refrigerant is depressurized by the indoor expansion valve 8, the refrigerant flows into the heat absorber 9 and evaporates. At this time, the moisture in the air blown out from the indoor blower 27 condenses and adheres to the heat sink 9, so that the air is cooled and dehumidified.
  • the refrigerant evaporated by the heat absorber 9 passes through the internal heat exchanger 19 and the evaporation pressure adjusting valve 70 sequentially, joins with the refrigerant from the refrigerant pipe 13D in the refrigerant pipe 13C, and then passes through the accumulator 12 and is sucked into the compressor 2 repeat.
  • the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, whereby dehumidifying and heating of the vehicle interior is performed.
  • the air conditioning controller 20 transmits the target heater temperature TCO (target value of the heating temperature TH) calculated from the target outlet temperature TAO to the heat pump controller 32.
  • the heat pump controller 32 calculates a target radiator pressure PCO (a target value of the radiator pressure PCI) from the target heater temperature TCO, and the refrigerant of the radiator 4 detected by the target radiator pressure PCO and the radiator pressure sensor 47
  • the rotation speed NC of the compressor 2 is controlled based on the pressure (radiator pressure PCI, high pressure of the refrigerant circuit R), and heating by the radiator 4 is controlled.
  • the heat pump controller 32 controls the degree of opening of the outdoor expansion valve 6 based on the temperature Te of the heat absorber 9 detected by the heat absorber temperature sensor 48 and the target heat absorber temperature TEO transmitted from the air conditioning controller 20. Further, the heat pump controller 32 opens the evaporation pressure control valve 70 (enlarges the flow path) / closes (a small amount of refrigerant flows) based on the temperature Te of the heat absorber 9 detected by the heat absorber temperature sensor 48. Prevent the problem of freezing due to too low temperature. (13) Internal cycle mode of vehicle air conditioner 1 in FIG. 9 In internal cycle mode, the heat pump controller 32 fully closes the outdoor expansion valve 6 in the dehumidifying and heating mode (fully closed position), Close the solenoid valve 21.
  • the radiator 4 By closing the outdoor expansion valve 6 and the solenoid valve 21, the inflow of the refrigerant to the outdoor heat exchanger 7 and the outflow of the refrigerant from the outdoor heat exchanger 7 are prevented, so the radiator 4
  • the condensed refrigerant flowing through the refrigerant pipe 13E passes through the solenoid valve 22 and all flows to the second bypass pipe 13F.
  • the refrigerant flowing through the second bypass pipe 13F passes from the refrigerant pipe 13B to the indoor expansion valve 8 through the internal heat exchanger 19. After the refrigerant is depressurized by the indoor expansion valve 8, the refrigerant flows into the heat absorber 9 and evaporates.
  • the moisture in the air blown out from the indoor blower 27 condenses and adheres to the heat sink 9, so that the air is cooled and dehumidified.
  • the refrigerant evaporated by the heat absorber 9 flows through the refrigerant pipe 13C sequentially through the internal heat exchanger 19 and the evaporation pressure adjusting valve 70, and repeats the circulation sucked into the compressor 2 through the accumulator 12.
  • the air dehumidified by the heat absorber 9 is reheated in the process of passing through the radiator 4, this means that dehumidifying and heating of the passenger compartment is performed, but in this internal cycle mode, the air flow on the indoor side Since the refrigerant is circulated between the radiator 4 (heat radiation) and the heat absorber 9 (heat absorption) in the passage 3, heating of heat from the outside air is not performed, and heating for the power consumption of the compressor 2 is performed.
  • the dehumidifying ability is higher than the dehumidifying and heating mode, but the heating ability is lowered.
  • the air conditioning controller 20 transmits the target heater temperature TCO (target value of the heating temperature TH) calculated from the target blowing temperature TAO to the heat pump controller 32.
  • the heat pump controller 32 calculates a target radiator pressure PCO (target value of the radiator pressure PCI) from the transmitted target heater temperature TCO, and the target radiator pressure PCO and the radiator 4 detected by the radiator pressure sensor 47
  • the rotation speed NC of the compressor 2 is controlled based on the refrigerant pressure (the radiator pressure PCI, the high pressure of the refrigerant circuit R), and the heating by the radiator 4 is controlled.
  • the auxiliary heating device is not limited to the auxiliary heater 23 shown in the embodiment, and a heat medium circulation circuit which heats the air in the air flow passage 3 by circulating a heat medium heated by the heater and an engine You may utilize the heater core etc. which circulate the heated radiator water.
  • Air conditioner 1 Vehicle air conditioner 2 Compressor 3 Air flow passage 4 Radiator 6 Outdoor expansion valve 7 Outdoor heat exchanger 8 Indoor expansion valve 9 Heat sink 10 HVAC unit 11 Control device 20 Air conditioning controller 23 Auxiliary heater (auxiliary heating device) 27 Indoor blower (blower fan) 28 air mix damper 32 heat pump controller 53 air conditioning control unit 65 vehicle communication bus 75 battery R refrigerant circuit

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  • Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Thermal Sciences (AREA)
  • General Engineering & Computer Science (AREA)
  • Chemical & Material Sciences (AREA)
  • Combustion & Propulsion (AREA)
  • Air-Conditioning For Vehicles (AREA)

Abstract

L'invention porte sur un dispositif de climatisation de véhicule capable de supprimer, au moyen d'une commande relativement simple, une diminution du confort dans une cabine de véhicule et une diminution de l'efficacité de fonctionnement due à la formation de givre sur un échangeur de chaleur extérieur. La présente invention comprend un compresseur 2, un radiateur 4, un échangeur de chaleur extérieur 7 et un dispositif de commande, une opération de climatisation comprenant un mode de chauffage, dans lequel au moins le réfrigérant évacué du compresseur 2 dégage de la chaleur à travers le radiateur 4, et le réfrigérant à rayonnement thermique est dépressurisé et absorbe ensuite la chaleur à travers l'échangeur de chaleur extérieur 7, chauffant ainsi l'intérieur de l'habitacle du véhicule, s'effectuant à l'aide du dispositif de commande. Le dispositif de commande effectue le dégivrage de l'échangeur de chaleur extérieur 7 à chaque arrêt de l'opération de climatisation dans le mode de chauffage.
PCT/JP2018/023916 2017-07-18 2018-06-18 Dispositif de climatisation de véhicule Ceased WO2019017149A1 (fr)

Applications Claiming Priority (2)

Application Number Priority Date Filing Date Title
JP2017-138978 2017-07-18
JP2017138978A JP2019018708A (ja) 2017-07-18 2017-07-18 車両用空気調和装置

Publications (1)

Publication Number Publication Date
WO2019017149A1 true WO2019017149A1 (fr) 2019-01-24

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WO (1) WO2019017149A1 (fr)

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CN113853313A (zh) * 2019-05-28 2021-12-28 三电汽车空调系统株式会社 车辆用空气调节装置
CN115703323A (zh) * 2021-08-06 2023-02-17 本田技研工业株式会社 车辆用空调装置
CN119222825A (zh) * 2023-06-30 2024-12-31 美的集团股份有限公司 热泵系统的控制方法、热泵系统以及存储介质

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JP2022148724A (ja) * 2021-03-24 2022-10-06 サンデン・オートモーティブクライメイトシステム株式会社 車両用空調装置

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JPH07186710A (ja) * 1993-12-27 1995-07-25 Nippondenso Co Ltd 電気自動車用空気調和装置
JPH08268031A (ja) * 1995-03-31 1996-10-15 Nippondenso Co Ltd 車両用空調装置
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JP2013129353A (ja) * 2011-12-22 2013-07-04 Mitsubishi Heavy Ind Ltd 車両用空調装置
JP2014088152A (ja) * 2012-10-31 2014-05-15 Mitsubishi Motors Corp 車両用空調装置

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JPH05162535A (ja) * 1991-12-10 1993-06-29 Hitachi Ltd 自動車用空気調和装置
JPH07186710A (ja) * 1993-12-27 1995-07-25 Nippondenso Co Ltd 電気自動車用空気調和装置
JPH08268031A (ja) * 1995-03-31 1996-10-15 Nippondenso Co Ltd 車両用空調装置
US5791407A (en) * 1995-06-15 1998-08-11 Rapids Defrost System, Inc. Remote and programmable indash defrost/cooling system
JP2013129353A (ja) * 2011-12-22 2013-07-04 Mitsubishi Heavy Ind Ltd 車両用空調装置
JP2014088152A (ja) * 2012-10-31 2014-05-15 Mitsubishi Motors Corp 車両用空調装置

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* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN113853313A (zh) * 2019-05-28 2021-12-28 三电汽车空调系统株式会社 车辆用空气调节装置
CN115703323A (zh) * 2021-08-06 2023-02-17 本田技研工业株式会社 车辆用空调装置
CN115703323B (zh) * 2021-08-06 2025-08-22 本田技研工业株式会社 车辆用空调装置
CN119222825A (zh) * 2023-06-30 2024-12-31 美的集团股份有限公司 热泵系统的控制方法、热泵系统以及存储介质

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